Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
  • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
  • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
  • F16C19/10—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for axial load mainly
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
  • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
  • F16C19/52—Bearings with rolling contact, for exclusively rotary movement with devices affected by abnormal or undesired conditions
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
  • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
  • F16C19/54—Systems consisting of a plurality of bearings with rolling friction
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
  • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
  • F16C19/54—Systems consisting of a plurality of bearings with rolling friction
  • F16C19/55—Systems consisting of a plurality of bearings with rolling friction with intermediate floating or independently-driven rings rotating at reduced speed or with other differential ball or roller bearings
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
  • F16C2300/00—Application independent of particular apparatuses
  • F16C2300/20—Application independent of particular apparatuses related to type of movement
  • F16C2300/28—Reciprocating movement
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
  • F16C2360/00—Engines or pumps
  • F16C2360/46—Fans, e.g. ventilators
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
  • F16C41/00—Other accessories, e.g. devices integrated in the bearing not relating to the bearing function as such
  • F16C41/001—Integrated brakes or clutches for stopping or coupling the relatively movable parts

Definitions

• This invention relates to a rolling bearing device for taking up axial thrust forces; comprising two coaxially arranged thrust bearings series-connected with respect to their load, each bearing having a separate frictional locking device preventing that bearing from rotating in one or the other direction of rotation, respectively.
• Each frictional locking device includes a set of clamping bodies located between opposed first and second clamping surface portions each of which is immovable relative to a first and a second bearing track, respectively, of the associated bearing when the bearing is subjected to axial load.
• the first clamping surface portion of each locking device is provided in an element which is common to both bearings and which during axial load retains one bearing track of one bearing relative to one bearing track of the other bearing.
• the frictional locking device of each bearing comprises a clamping member, preferably in the form of a helical spring which, by exerting a lateral pressure, clamps one or the other of the two outer bearing races to a coupling member in fixed connection with those tracks of the two bearings which are adjacent to one another.
• the clamping members consists of helical springs
• a helical spring which in response to a rotational movement of the bearing in one direction is tightened so as to exert said clamping action, may, during the opposed releasing movement, show a tendency towards rotating its first loosened winding to a larger diameter so that the centrifugal force may press it up above the superjacent windings.
• the known helical springs employed as clamping members are pre-tensioned in order to obtain a sufficiently low hysteresis in the locking function. Then the friction within the bearing becomes relatively high during a movement opposite to the locking direction and it will also depend on the state of lubrication of the springs.
• each of said first clamping surface portions provided in said common element includes a number of first clamping surfaces having generatrices parallel to the axis of the bearing device; that each first clamping surface is located directly radially opposite and spaced from a cylindric second clamping surface oriented parallel to the axis of the bearing device and in connection with the second bearing track of the associated bearing; and that one of said radially opposed first and second clamping surfaces cooperating with either set of clamping bodies is formed by the radially inner or outer peripheral surface of a bearing race of the bearing in guestion.
• the bearing device is constructed such that both bearings are standard thrust bearings having the same diameter, and that the common element is formed as a retaining ring located internally of the bearings and having a radially protrudring flange located between the adjacent bearing races of the two bearings and in contact therewith.
• the bearing device has a minimal mounting diameter and that its manufacture is simple and cheap.
• Fig. 1 is a perspective and partly sectioned view of an embodiment of a bearing device according to the invention
• Fig. 2 is a schematic illustration of the functioning of a frictional locking device applicable in the bearing device of Fig. 1
• Fig. 3 is a schematic view of a second embodiment of a bearing device according to the invention.
• Fig. 4 is a schematic cross section through a third embodiment of a bearing device according to the invention
• Fig. 5 is a schematically shown cross section through a fourth embodiment of a bearing device according to the invention.
• Fig. 6 is a very schematic fractional view, in cross section and on a larger scale, of a frictional locking device applicable in the bearing device shown in Fig. 5.
• a rolling bearing device comprising a common element 1 formed as a retaining ring 2 having a centrally arranged and radially protruding flange 3, and two standard thrust bearings 4, 5 of equal diameters and located on opposite sides of flange 3.
• the fit between retaining ring 2 and the two bearing races 6 adjacent flange 3 shall have a character such that the bearings are sufficiently centered, but it need not be a press fit which retains the bearing races 6 relative to the retaining ring because the friction resulting from the axial load on the bearing will retain them to flange 3.
• the diameter of retaining ring 2 has been reduced so that there is a clearance between races 7 and retaining ring 2 in said regions which constitute clamping surface portions of ring 2.
• Each thrust bearing 4, 5 is associated with a frictional locking device which includes a plurality of recesses 8 formed in the clamping surface portion of ring 2 opposite the bearing race 7.
• Each recess 8 houses a clamping roller 9 which is pre-loaded, by a compression spring 10 located in a bore 11 at the large end of the recess, towards the narrow end of the recess and thus outwardly towards bearing race 7.
• a pair of opposed clamping surfaces cooperating with each clamping roller 9 comprises the radially inner peripheral surface of race 7 which is a circular cylinder surface the generatrix of which is parallel to the axis of the bearing device, and the outer lateral surface of the recess the generatrix of which is likewise parallel to the bearing axis.
• bearing race 7 If bearing race 7 is rotated in the locking direction, i.e. relative to retaining ring 2 such that rollers 9 are shifted towards the narrow ends of the recesses, the rollers will be fractionally coupled to the opposed clamping surfaces, thereby retaining race 7. Because the rollers are operative between clamping surfaces which are parallel to the bearing axis, the locking function is independent of the axial load on the bearing and thus it is possible to provide a practically hysteresis-free locking function with a low release torque and a high brake torque.
• this embodiment of the bearing device particularly suited for use as a blade suspension bearing in an axial flow fan in which the blade angle is adjustable during operation, because such bearings are heavily loaded in axial direction and at the same time the changes of the blade angles during operation are small.
• a rotation of the blade opposite the locking direction of one bearing will rotate one bearing race 7 relative to the common element, and the associated balls will thus be shifted to a different position along the bearing tracks of that bearing while simultaneously the other set of rollers 9 retain the other bearing race 7 relative to the common element.
• Fig. 2 there is shown a fractional view for illustrating the frictional locking device in more detail.
• a roller 9 which, via a thrust pin 13, is urged towards the narrow end of the recess and outwardly against the radially oriented clamping surface on bearing race 7 by spring 10.
• the wedge angle of the recess and the materials employed may be designed and chosen in a manner known from frictional locing devices associated with radial bearings.
• Roller 9 is spring-loaded in order to ensure the locking function and to provide a low hysteresis, and the spring force is chosen such dependent on the relevant operational conditions of the bearing device, that the forces to which the locking device is subjected in use are balanced.
• clamping bodies which may either be free, spring-loaded or supported in an annular holder, such as cylindric bodies having an asymmetric cross section.
• clamping bodies have been shown as spring-loaded rollers 9 located in recesses, but cylindric bodies with an asymmetric cross section may also be used, but in that case the clamping surfaces on element 16 would be designed as by and large circular cylindric clamping surfaces coaxial with the bearing.
• the common element may comprise only the intermediate bearing race 15, in which case the clamping bodies would be operative between the radially outer edge surface of the race and a bearing housing, and between the radially inner edge surface of the race and a shaft, respectively.
• Fig. 4 there has been shown a counter- rotating bearing having a minimal mounting height and a relatively large diameter. The two axial bearings are located in the same radial plane and have different diameters.
• a bearing track 18 and 19 there has been formed a bearing track 18 and 19, respectively, associated with either bearing and opposite those tracks each bearing has a bearing race 20 and 21, respectively, the rotation of which in the respective locking direction is prevented by clamping bodies, such as the rollers 9 which are operative between opposed clamping surfaces which are coaxial with the bearing and by and large circular cylindric.
• This bearing is, inter alia, well suited for supporting the arms of a windmill in a hub, because this requires a low mounting depth.
• two standard axial thrust bearings 22, 23 are arranged at opposite sides of a protruding flange on a substantially circular cylindric common element 24 which at either end is formed with an end portion 30 or 31, respectively, of somewhat smaller diameter.
• clamping bodies cylindric bodies of asymmetric cross section have been inserted between each of those end portions and the opposed bearing races 25.
• clamping bodies 26 may be supported in a cage 27 which, if desired, may exert a preloading force on the bodies so that the locking function operates at all operational conditions.
• the clamping bodies may e.g. be of type FE 400 commercially available from the company Georg Müller N ⁇ rnberg GmbH or the type known from Fig. 7 of DE-P 3 245 347.
• the bearing races 25 remote from one another may be internally machined in order to obtain a sufficiently fine tolerance on the inner diameter and an ensuing good effect of the locking function. This may be necessary because to-day many standard bearings are manufactured so as to be retained at the outer diameter.
• the inner diameter of the common element may be increased as compared to the embodiment of Fig. 1.
• a removable locking ring 28 located in the groove ensures that the clamping bodies remain in place during manipulation of the bearing.
• Any of the common elements mentioned above may after machining be hardened in a known manner so that there is obtained a hardness of the material of the element which is suitable for taking up the pressure exerted by the clamping bodies. As a result larger deformations of the element are avoided and a long lifetime thereof is ensured.
• clamping bodies with asymmetric cross section may be used in all the embodiments shown, and that the invention is not limited to the use of ball bearings, since any type of rolling bearings, e.g. roller bearings or needle bearings, can be used.
• the bearing device according to the invention can to advantage be employed at any place where heavily loaded axial bearings are subjected to small swivelling movements which may result in "brinelling" of the bearing tracks, such as in propeller hubs, thrust bearings for rudder suspensions in ships, or steering gear suspensions in automobiles.

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• Engineering & Computer Science (AREA)
• General Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• Rolling Contact Bearings (AREA)
• Support Of The Bearing (AREA)

Applications Claiming Priority (2)

Publications (1)

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ID=8148207

Family Applications (1)

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Citations (4)

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• 1986
  • 1986-12-22 DK DK623386A patent/DK623386A/da not_active Application Discontinuation
• 1987
  • 1987-12-18 AU AU10841/88A patent/AU1084188A/en not_active Abandoned
  • 1987-12-18 WO PCT/DK1987/000161 patent/WO1988004739A1/en unknown
  • 1987-12-18 EP EP87311186A patent/EP0272892A3/en not_active Withdrawn

Patent Citations (4)

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